Pump mechanism and control therefor



June 11, 1963 A. ROTH 3,093,237

PUMP MECHANISM AND CONTROL THEREFOR Filed March 29. 1961 6 Sheets-Sheet 1 I08 no INVENTQR [\Qma Pom WQn fwwd ATTORNEYS 6 Sheets-Sheet 2 Filed March 29. 1961 Fig. 2

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PUMP MECHANISM AND CONTROL THEREFOR Filed March 29, 1961 6 Sheets-Sheet 5 INVENTOR Amu E 9 ATTORNEY June 11, 1963 A. ROTH 3,093,237

PUMP MECHANISM AND CONTROL THEREFOR Filed March 29, 1961 6 Sheets-Sheet 4 Fi 4 rum m m 2 I'H" I 34 m "B l8 4 "7 ,II? "a 84 ,9o

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6 Sheets-Sheet 5 ATTORNEY 5' June 11, 1963 Filed March 29. 1961 A. ROTH 3,093,237

PUMP MECHANISM AND CONTROL THEREFOR 6 Sheets-Sheet 6 Fig.9

INVENTOR Ammz- Dom ATTORNEYS United States Patent 3,693,237 PUMP MECHANISM AND CQNTROI. THEREFBR Artur Roth, Philadelphia, Pa., assignor to Lanston Industries, Incorporated, Philadelphia, Pin, a corporation of Virginia Filed Mar. 29, 1961, Ser. No. 99,217 26 Ciairns. (Cl. 199-52) This invention relates to pump mechanisms and more particularly to pump mechanisms of the type adapted to eject molten metal into a type mold embodied in casting machines of the type manufactured under the trademark Monotype.

Monotype casting machines have been available commercially for many years and ofier the advantage of extreme versatility in that each type character is individually cast in the normal operation of the machine. A disclosure of an early embodiment of a machine of this type may be found in US. Patent No. 625,998 issued May 30, 1899, to Bancroft. More detailed disclosure of a more recent embodiment can be found in the publication The Monotype Casting Machine Manual published in 1952 by the National Committee of Monotype Users Associates London and the Monotype Corporation Limited, London. One of the basic component elements of type casting machines of the type mentioned above is the pump mechanism utilized to eject molten type metal into the mold cavity of the machine to cast the individual type characters.

While single character type casting machines provide the advantage of flexibility and versatility, they are inherently restricted in the maximum speed at which they can operate by the time required to get the molten type metal into the mold cavity and solidified so that the mold cavity can be cleared for the next cast. The pump mechanisms heretofore employed have been of the reciprocating type employing a nozzle which engages within a recess in the mold during each pumping cycle. These pump mechanisms are operated in such a way that the nozzle engages within the recess prior to the actual ejection or movement of the molten type metal into the mold cavity or prior to the movement of the pump plunger to eiIect ejection of the type metal. With the prior art pump mechanisms, the head of molten type metal within the pump nozzle is disposed somewhat below the end of the nozzle prior to the ejection stroke, thus resulting in the movement of the volume of air above the head of molten metal into the mold cavity before the molten type metal is ejected therein. This volume of air which is ejected into the mold cavity must be evacuated from the mold cavity as the molten type metal is ejected therein and thus presents problems of undue porosity of the type cast. Moreover, since an added volume of air is ejected into the mold cavity prior to the actual ejection of the molten type metal, the evacuation of this added air which enters under compression tends to impose an added limitation to the speed at which the machine can operate.

An object of the present invention is the provision of a pump mechanism of the type described which is operable to begin the actual movement of the molten metal to the end of the nozzle prior to the engagement of the nozzle with the mold recess, thus dissipating the air volume in the end of the nozzle inherent in the operation of the prior art machines to the atmosphere and enabling the machine to either operate at a higher speed or at lower speeds with an attendent decrease in the porosity of the type cast.

Still another object of the present invention is the provision of a pump mechanism of the type described having an improved compound linkage for effecting sequential movement of the pump piston, so as to insure that the Patented June 11, 1963 "ice type metal will be moved to the end of the pump nozzle, then the pump body into cooperative engagement with the mold recess, and then subsequent movement of the pump plunger or piston to eject the molten type metal into the mold cavity.

Still another object of the present invention is the pro vision of a pump mechanism of the type described having improved means forcyclically actuating the same.

In the operation of an individual type casting machine, a character is cast on each revolution of the main cam shaft, although two revolutions of the main cam shaft of the machine are required for all of the actions necessary to produce each cast character. The mechanism for accomplishing these purposes are adequately disclosed in the above-mentioned Bancroft patent and Mono-type publication. However, there are certain operations where it is required that the pump be ineffective to eject a charge of molten type metal so that there will be no character cast during the given revolution. Consequently, during the operation of the machine, the input signal for any given character must be delayed or otherwise transmitted to the pump mechanism one revolution after the revolution in which the signal is put in or received.

Accordingly, it is another object of the present invention to provide an improved mechanism effective to control the operation of the pump mechanism, a time delay of one revolution after the signal has been received.

These and other objects of the present invention will become more apparent during the course of the following detailed description and appended claims.

The invention may best be understood with reference to the accompanying drawings wherein an illustrative embodiment is shown.

In the drawings:

FIGURE 1 is a side elevation view, with parts broken away, of a pump mechanism embodying the principles of the present invention showing the same applied to a type casting machine;

FIGURE 2 is a rear elevational view, with parts broken away, of the structure shown in FIGURE 1;

FIGURE 3 is a top plan view of the structure shown in FIGURE 1;

FIGURE 4 is an enlarged fragmentary sectional view taken along the line 4-4 of FIGURE 3, showing the position of the pump parts at the start of the ejection stroke;

FIGURE 5 is a view similar to the FIGURE 4 showing the position of the pump parts during the ejection stroke just prior to the engagement of the nozzle with the mold;

FIGURE 6 is an enlarged fragmentary sectional view taken along the line 6-6 of FIGURE 3;

FIGURE 7 is an enlarged fragmentary sectional view taken along the line 7--7 of FIGURE 2, showing the position of the parts in an inoperative position such as when a second successive justification signal has been received;

FIGURE 8 is a view similar to FIGURE 7 showing the position of the parts after a character signal has been received;

FIGURE 9 is a view similar to FIGURE 7 showing the position of the parts in their normal operative position, the second revolution after a character signal has been received; and

FIGURE 10 is a sectional view taken along the line Ill-10 of FIGURE 7.

Referring now more particularly to the drawings, there is shown in FIGURES 1-3 a pump mechanism generally indicated at 10 which embodies the principles of the present invention. The pump mechanism 10 is shown applied to a Monotype casting machine, the frame of which is generally indicated by the numeral 12. The pump mechanism 10 is adapted to cooperate with a type metal melting pot, generally indicated at 14, which is of conventional construction and embodies the usual heating elements which can 'be energized to melt type metal placed in the pot 14 to a molten condition so that it can be drawn from the pot 14 by the pump mechanism 10 and ejected into the mold of the casting machine, generally indicated at 16.

The pump mechanism 10 itself comprises a pump assembly 18 which is suitably carried by the type metal pot 14 in operative relation therewith. The pump assembly 18 is actuated through a conventional pumping cycle by means of a fluid pressure device, generally indicated at 20, the device being operatively connected with the pump assembly 18 to actuate the same by means of a novel motion transmitting mechanism, generally indicated at 22. The fluid pressure device 20 is, in turn, actuated by a valve mechanism, generally indicated at 24, and the valve mechanism is controlled by a holding or delay linkage mechanism 26. The linkage mechanism 26, is, in turn, adapted to be actuated by conventional structure provided on the usual Monotype casting machine and is operable in response to the various movements which occur during the normal operation of the machine to effect a desired correlated movement of the pump assembly 18 through the operation of the valve mechanism 24, the fluid pressure device 20 and the motion transmitting mechanism '22.

As is usual, the melting pot 14- is mounted on the main frame 12 of the machine both for up and down and for arcuate swinging movement about a vertical axis so that the pump assembly 18 carried thereby can be moved'between an inoperative access position disposed laterally out from the frame of the machine and an operative position wherein the pump assembly 18 is disposed beneath and closely adjacent to the mold 16. To this end, a bracket 28 is suitably bolted or otherwise rigidly secured to the main frame 12 of the machine, the bracket providing upper and lower laterally extending flanges 30 and 32. Journaled in the outer end of the flanges is a vertical shaft 34, the central portion of which has a worm thread 36 formed on the outer periphery thereof. Mounted on the shaft 34 for vertical movement with respect thereto between the flanges 30 and 32 is a mounting arm 38 to which the melting pot 14 is fixed by an suitable means, such as bolts or the like.

Formed on the arm 38 and extending upwardly therefrom at an angle with respect to the vertical is an elongated guide portion 40, the outer end of which is apertured' to receive the upper end portion of a shaft or elongated guide portion 46, the outer end of which is apertured to receive the upper end portion of a shaft or elongated rod 42. The shaft 42 extends-alongside the guide portion 40 and has its lower end suitably journaled in the arm 38 at a position adjacent the threaded shaftSd. Formed on the shaft 42 adjacent its lower end is a helical pinion 44 which meshes with the-threads 36021 the shaft 34. The upper end of the shaft 42 has afdxed thereto a lever arm 46 having a handle 48 rotatably mounted on the outer end thereof. It can be seen that by turning the arm 46 with the handle-48 so as to rotate the shaft 4-2, the mounting arm 38 will be moved vertically along the shaft 34 between the bracket flanges 30 and 32. In addition, the mounting arm may also be swung or pivoted about the axis of the threaded shaft 34. In this way, the type metal melting pot 14 and the pump assembly 18 carried thereby may be moved between its inoperative position disposed outwardly of the frame 12 of the casting machine and its operative position disposed below the mold 16.

As best shown in FIGURES 4 and 5, the pump assembly 18 comprises a pump body 50 providing a vertical cylindrical portion 52, an outwardly extending lateral portion 54 and a nozzle portion 56 extending vertically from the outer end of the lateral portion 54. The cylindrical portion 52 of the pump body 50 defines a cylinders or pump chamber 58having an inlet opening 60 exending laterally therein, as best shown in FIGURE 6. The pump chamber 58 has a suitable float valve 62 mounted therein which has a bleed orifice 63 formed in the lower end thereof as shown in FIGURE 6.

Formed in the lateral portion 54 of the pump body 50 is an elongated passage 64 which communicates at one end with the cylinder 58 and at its other end with a bore 66 extending vertically through the nozzle portion 56. The upper end of the bore 66 communicates with a nozzle member 70 threaded or otherwise suitably secured to the upper end of the nozzle portion 56. Threadedly engaged within the lower end of the bore 66 is an elongated hollow barrel or cylinder 68, the upper end portion of which communicates with the bore 66 through a restricted passage 69 formed therein. Slidably mounted within the barrel 68 is a plunger 72, the upper end of which is spaced below the passage 69 therein and the lower end of which extends below the lower end of the barrel 63. The plunger is retained within the barrel 68 by any suitable means such as a vertically elongated transversely extending aperture 74 through which a cotter pin 76 extends, the latter also extending through suitable apertures formed in the lower end of the barrel 68. It can be seen that the cotter pin 76 arrangement is such that the plunger 72 can have limited longitudinal movement within the barrel 68.

In order to induce the fiow of molten type metal through the inlet opening 60and to force the molten type metal from the cylinder 58 through the passage 64 and out through the nozzle 70, a piston or plunger 78 is mounted within the cylinder 58 for vertical reciprocating movement. The piston 78 has the usual piston rod 80 fixed thereto and extending upwardly therefrom through the upper end of the cylinder portion 52 of the pump body 50.

The cylindrical portion 52 of the pump body 50 has integrally formed thereon a pair of outwardly diverging generally radially extending arm portions 82 which have fixed to the outer ends thereof a pair of mounting arms 84. The mounting arms 34 extend over a pair of cooperating mounting brackets 86, fixed to the melting pot 14 by any suitable means, such as bolts or the like. Extending upwardly from the mounting brackets 86 is a pair of. bolts 88, the upper ends of which seat within appropriate recesses 90 formed in the lower surfaces of the associated mounting arms 84. The engagement of the bolts within the recesses 90 serves to mount the pump assembly 18 for pivotal movement'with respect to the melting pot 14 about a generally horizontal axis. A pair of coil springs 92 are connected between the mounting arms 84 and mounting brackets 86, as by bolts 94 so as to counterbalance to some extent the weight of the pump assembly 18 and permit the latter to be moved more easily in a clockwise direction, as viewed in FIG- URES 4 and 5.

The fluid-pressure device 20 preferably comprises a conventional pneumatic double acting piston and cylinder unit including the usual cylinder 96 having a piston 98 slidably mounted therein. Secured to the piston 98 is a piston rod 100 which extends from one side of the pis' ton 9S outwardly through one end of the cylinder 96.

As best shown in FIGURES 1 and 2, the outer end of the piston rod 100 extends upwardly and has a coil spring 102 mounted in surrounding relation thereto, one end of which engages the outer end of the cylinder 96 and the opposite end of which engages a washered nut 104 on the extremity of the piston rod. The not 104 also serves to secure to the outer end of the piston rod 100 an elongated rod 106 which extends upwardly through suitable openings formed in the bracket flanges 30 and 32 and connects with and forms a part of the motion transmitting mechanism 22. Preferably, as assist coil spring 107 is mounted in surrounding relation to the rod 106 between the lower flange 32 and a suitable collar adjustably fixed to the rod 106 in the spaced relation to the flange 32.

As best shown in FIGURES 1-3 the motion transmitting mechanism 22 includes a pump plunger actuating lever arm 108, one end of which is pivotally connected with the upper end of the rod 106 through a swivel clevis, as indicated at 110, and the opposite end of which is bifurcated and formed with rounded cam-like extremities 111 mounted within opposed transversely extending slots 112, formed in the upper end of the piston rod 80, for transverse sliding and arcuate pivotal movement with respect thereto, with the upper end of the pump piston rod 80. Preferably, the pump piston rod 80 has a handle 114 rotatably mounted therein at a position above the slots 112.

The motion transmitting mechanism 22 also includes a pump body actuating lever arm 116 which is disposed below and in generally parallel relation with respect to the lever arm 108. One end of the lever arm 116 is bifurcated and formed with rounded cam-like extremities 117 which, like the extremities 111 of the arm 108, are mounted within opposed slots 118, formed in the upper end of the cylindrical portion of the pump body, for transverse sliding and arcuate pivotal movement with respect thereto. The opposite end of the lever arm 116 is pivotally connected, as at 120, to a swivel bracket 122. As is clearly shown in FIGURE 3, the end portion of the lever arm 116 adjacent the pivot 120 is bifurcated into a circular configuration, as indicated at 124, to permit the passage of the upper end of the rod 106 therethrough. The swivel bracket 122 is mounted for rotation about the axis \of the rod 106, as by an integral collar portion 123 extending upwardly from the bracket 30 in concentric relation to the rod 106, so as to permit the motion transmitting mechanism 22 including the lever arms 108 and 116 to be separately swung or pivoted about the axis of the rod 166 from a laterally extending inoperative position to an operative position in cooperation with the pump assembly 18, as shown, when the latter is disposed in its operative position beneath the mold 16. It will be noted that due to the offset relation between the vertical swinging axis of the melting pot and pump assembly and the vertical swinging axis of the motion transmitting mechanism 22, the bifurcated extremities 111 and 117 of the lever arms 1G8 and 116 of the latter will be moved outwardly from engagement with their slots 1-12 and 118 respectively when the pot is moved from its operative position to its inoperative position.

The motion transmitting mechanism 22 also includes a link 128 which extends vertically between the lever arms 103 and 116 and has its ends pivotally interconnected with the latter at positions adjacent the central portions thereof, as indicated at 130 and 132.

Operation of the Pump Mechanism The motion transmitting mechanism 22 is effective to move the pump assembly 18 through a cycle of operation which includes an initial downward movement of the pump plunger or piston rod into the cylinder, 21 subsequent upward movement of the pump body 50 with respect to the melting pot 14 until the nozzle member 70 engages a nozzle receiving recess 134 in the mold, and a subsequent downward movement of the pump piston within the cylinder to effect an ejection of molten type metal into the cavity of the mold 16 in response to the movement of the piston 98 within the air cylinder 96 in an upward direction. On the downward or return stroke of the piston 98, the pump body is moved downwardly until the nozzle 70 is spaced below the mold recess 134 and the pump piston is moved upwardly with respect to the cylinder to draw in molten type metal from the melting pot 14 through the inlet opening 60 to recharge the cylinder with the molten type metal.

The pump assembly 18 is effective to eject molten type metal from the nozzle member 70 during the downward movement of the pump plunger and to re-charge the pump cylinder during the upward movement of the pump plunger in the following manner. It will be noted that when the pump plunger is disposed in its uppermost position, as shown in FIGURE 4, the float valve 62 is seated within the pump head 50 between the inlet opening 60 and the passage 64 and the pump plunger is disposed in a position above the inlet opening 60. Upon initial downward movement of the pump plunger, the float valve 62 will move out of its sealed position and there will be a slight movement of molten type metal through the passage 64 and the passage of the nozzle member 70. Also during this initial movement, there will be some loss of molten metal from the pump chamber into the inlet opening 60 until the pump'chamber reaches a position sufiicient to close the latter. At this point, full pressure is applied by the pump plunger to the molten metal within the pump chamber to move the same past the float valve 62, through the passage 64 and out through the nozzle member 70. On the return or upward stroke of the pump plunger, the fioat valve 62 is initially sealingly engaged within the pump body between the passage 64 and opening 60 so that the molten metal within the passage 64 and nozzle 70 can not flow back into the pump chamber. It will be noted, however, that due to the provision of the bleed orifice 63 a small quantity of flow of this metal is allowed to take place so that the level of the molten metal within the nozzle will be disposed below the upper end thereof. Upon further upward movement of the pump plunger the inlet opening 60 will be uncovered and metal will be allowed to fiow through this opening to re-charge the pump cylinder.

The provision of the bleed orifice '63 within the float valve 62 is provided in the present pump assembly merely as an added safety factor to insure against solidification of metal in the extremity of the nozzle opening because of its proximity to the cooled mold during operation. In the pump mechanisms previously employed, this action was essential because of the fact that the nozzle was in actual contact with the cooled mold prior to ejection and solidification sometimes resulted. With the present pump mechanism, the time in which the nozzle is actually in engagement with the mold and no ejection is taking place is reduced to an absolute minimum so that the orifice 63 can be eliminated if desired, although, as indicated above, it is preferred as an additional safety factor. Q

The significant operational advantage of the motion transmitting mechanism 22 is that there is accomplished an initial downward movement or pumping movement of the pump piston prior to the engagement of the nozzle 70 with the mold recess 134. This action is clearly illustrated in FIGURES 4 and 5. FIGURE 4 illustrates the position of the pump parts just prior to the beginning of the pumping stroke. FIGURE 5 illustrates the position of the parts after an initial upward movement of the piston 98 :of the device 20. It will be noted that in the position shown in FIGURE 4 a column of air A exists in the nozzle opening above the level of the molten metal. By beginning the pumping action prior to the movement of the nozzle into engagement with the mold recess 134, the column of air A is evacuated from the nozzle and allowed to dissipate into the atmosphere so that it will not be forced into the cavity of the mold 16 as would be the case if the nozzle engaged the mold recess 134 prior to the pumping action. With the present arrangement the initiation of the pump-ing stroke causes the upper level of the molten type metal to displace the column of air A from the upper end of the nozzle opening and there may even be some slight spillage of molten metal outwardly of the nozzle opening before the latter actually engages the mold recess 134.

This action is achieved by the motion transmitting mechanism 22 of the present invention by virtue of the arrangement of the lever arms 198 and 116 and the relative position of the pivots of the link 128 with respect to these lever arms. It will be noted that when the motion trans- 7 mitting mechanism 22 and pump assembly 13 are in their operative positions, the swivel bracket 28 affords a fixed .pivot 120 for the lever arm 116. Moreover, it will be noted that the weight of the pump assemblylS and the strength of the counterbalance springs 92 are such that the. pump body will normally assume a position with respect to the melting pot 14 in which the pump nozzle is disposed in spaced relation below the mold recess 134. In addition, the weight of the lever arms 198 and 116 and the connecting link 1255 also serve to provide a resistance to the movement of the pivot 130 between the connecting link and plunger actuating lever arm 168. Thus, the initial upward movement of the rod 106 will cause an initial pivotal movement of the plunger actuating lever arm 108 about the pivot 130, thus causing the pump piston rod 80 to move initially downwardly into the cylinder and initiate the movement or flow of molten type metal from the cylinder through the passage 64 to effect a displacement of the upper surface of the molten metal in the nozzle opening toward the extremity thereof in the manner indicated above.

It will be noted that the length of the plunger actuating lever arm 168between the pivots 110 and 130 is less than the length of the pump body actuating lever arm 116 between the pivots 120 and 132. Because of the greater length of the latter lever arm and the resistance of the molten type metal within the cylinder to the downward movement of the plunger, continued upward movement of the rod 106 will effect an upward swinging movement in a clockwise direction as viewed in FIGURE 1, of the pump body actuating lever arm 116 through the movement of the connecting link 128. This upward movement of the pump body actuating lever 116 results in an upward movement of the pump body 18 until the nozzle engages the mold recess 134.

While the action of the motion transmitting mecha nism 22 during the initial portion of the upward movement of the rod 106 has been indicated above as causing a sequential operation first of the pump plunger and then of the pump body 18, it will be understood that both of these movements are instantaneous so that they may either be sequential or substantially simultaneous. The important consideration is that the column of air A is displaced by the movement of the type metal before the nozzle engages the mold recess, as shown in FIGURE 5, so that the air A is not forced into the mold cavity ahead -of the molten-metal thus necessitating the evacuation of this additional volume of air from the mold cavitywith the attended disadvantage of either undue type porosity or undue operational speed restriction.

It will be understood that when the nozzle engages the mold recess further upward movement of the rod 106 will, of necessity, result in a pivotal'movement of the pump plunger actuating lever about the pivot 110 thus causing the plunger to move downwardly into the cylinder to move the molten metal through the passage 64 outwardly of the nozzle and into the cavity of the mold 16. The upward stroke of the piston 98 of the fluid pressure device is halted by the build up of pressure of the molten metal as it fills the cavity, thus preventing further downward movement of the pump plunger. Of course, the pressure applied to the main cylinder is as constant as possible and is held beneath a maximum value which would result in the application of excessive forces to the pump plunger. In this way, the amount of molten metal ejected into the cavity of the mold 16 is dependent upon the volume of the mold cavity itself and since the movement of the pump plunger results from the application of a constant force, such force can be readily controlled so as to provide for the complete filling of the largest cavity volume contemplated and yet not provide excessive forces which cannot be resisted when the smallest volume cavity has been filled.

Another important feature of the present pump mechmetal.

anism 10 is the provision of thenozzle plunger 72. 'It will be understood that the actuation of the main cylinder is related through the operation of *the valve mech anism 24 and linkage mechanism 26 to effect a pumping cycle, when it is desired to form type characters, during each revolution of the main cam shaft of the mechanism. Moreover, this cam shaft is driven by a variable speed drive so that the cyclic operation of the pump mechanism 22 can also be varied in speed. During high speed operation, the ejection of the molten metal into the mold cavitytakes place in such a short period of time that the reaction to the ejection of the material on the nozzle portion of the pump mechanism 22 is not sufficient to move the nozzle away from the mold recess due to the dynamic forces involved. Atlower operational speeds, however, where the dynamic forces are not so severe, there may be a tendency for the nozzle to move away from the mold recess during the actual ejection of the molten This tendency results from the natural tendency of any nozzle to react from the ejection of a fluid therefrom and is evident to anyone who has ever held a fire hose nozzle. It is the same as the jet principle utilized in rocketry.

The pump plunger 72 is provided to counteract the tendency of the pump nozzle to move away from the mold recess during ejection. It will be noted that the pressure of the molten metalwithin the nozzle also acts upon the upper end of the plunger 72, thus tending to move the latter downwardly until the lower end thereof engages the bottom of the melting pot 14. In this way, the plunger applies an equal pressure in a direction tending to move the nozzle into engagement with the mold recess and thus insures that the nozzle will not move out of engagement during the ejection of the molten metal.

The valve mechanism 24 may be of any suitable construction capable of reversing flow to a double acting pneumatic cylinder and piston unit. As shown, the valve mechanism 24 comprises a valve body 136 having a bore 138 extending longitudinally therethrough. Formed in the ends of the bore 133 is a pair of counterbores 140 and 142, the outer ends of which are covered by a pair of end plates 144 and 146 fixed to the ends of the valve body by any suitable means, such as bolts 148. Longitudinally slidably mounted within central bores formed in the end plates is a valve stem 150 which extends longitudinally through'the main bore of the valve body in concentric relation therewith. Fixed to the valve stem within the counterbore 140 is a disc-like valve member 152 having longitudinally-spaced O-ring seals 154 and 156 mounted on the periphery thereof within appropriate annular grooves. The valve stem has a second valve member 158 fixed thereto within the counterbore 142, the valve memher 158 being of construction similar to the valve member 152 and having a pair of O ring seals 160 and 162 mounted in appropriate annular grooves in the periphery thereof.

The valve body 136 includes a central inlet opening 164 which extends radially inwardly from the outer periphery thereof into communication with the main bore 138. It will be understood that the inlet 164 has suitable conduit 165 connected therewith which connects with a suitable source of air under pressure as, for example, an air compressor (not shown). The valve body also has formed therein an outlet opening 166 which extends from the outer periphery thereof radially inwardly into communication with the counterbore 140. The outlet 166 is connected :by a conduit 168 with lower end of the cylinder 96 ofthe fluid pressure device 20. In a like manner, the valve body 136 also has provided therein a second outlet opening '170 which extends from the outer periphery thereofradially into communication with the counterbore 142. The outlet 170 is communicated with the upper end of the cylinder 96 through a suitable conduit 172v The end of the valve stem 150 extending outwardly from the end plate 144 has mounted in surrounding relation thereto a coil spring 174, one end of which engages the exterior of the end plate 144 and the opposite end of which engages a washer 176 mounted on the valve stem. The exterior of the adjacent extremity of the valve stem is threaded to receive bolts .178 which serve to retain the washer on the valve stem in any desired position of adjustment. It will be seen that the coil spring 174 serves to resiliently bias the valve stem and hence the valve members 152 and 158 fixed thereto into a position in which the valve member 158 closes communication between the main bore 138 and counterbore 142 while the valve member 152 permits communication between the main bore 138 and the counterbore 140. In this way, the air under pressure in the inlet 164 is communicated with the outlet 166 and the outlet 170 communicates with associated ports 18% formed in the end plate 146. Thus, with the valve in the position shown, the piston rod 166 of the fluid pressure device 20 will be moved upwardly to actuate the pump mechanism.

The linkage mechanism 26 serves to effect movement of the valve mechanism from the spring-urged position shown to an opposite position wherein the O-ring seal 154 of the valve member .152 serves to close communication between the inlet 164 and the outlet 166 to permit the latter to exhaust through ports 182 formed in the end plate 144. The O-ring seal 162 of the valve member 168 prevents communication between the outlet 17% and the exhaust ports 180 while the inlet 164 is communicated with the latter. In this position the piston rod of the device 20 is moved downwardly.

The linkage mechanism 26 comprises a vertical cam shaft 184 which is suitably journaled on the main frame 12 of the casting machine.

It will be understood that the cam shaft 184 may be oscillated in timed relation in each revolution of the main cam shaft of the casting machine by any of the various mechanisms embodied in the casting machine which are cycled once per revolution. Preferably, the type pusher bar of the casting machine, indicated at 136, is utilized for this purpose in the present embodiment. As shown, the extremity of the type pusher bar opposite from the type engaging extremity thereof has a cam plate 188 adjustably fixed to the upper surface thereof by any suitable means, such as a bolt 1% extending through an elongated slot in the cam plate. The cam plate 188 is adapted to engage a cam roller v192 mounted on the outer end of an arm 194 fixed to the upper end of the cam shaft 184.

The lower end of the cam shaft is journaled on a suitable bracket 196 fixed to the main frame 12 of the casting machine in any suitable manner and has an arm 198 fixed lthereto. The outwardly extending end portion of the arm 1% is bifurcated and embraces a collar 200 mounted on a reduced end portion 202 of the valve stem extending outwardly from the end plate 146. It will be noted that one end of the collar is adapted to engage the shoulder formed by the junction of the end portion 202 to the main body of the valve stem and the opposite end of the collar is provided with a radially outwardly extending annular flange 204. The flange 204- is adapted to be engaged by enlarged, rounded portions 206 formed on the bifurcated outer end of the arm 198 at a position spaced inwardly from the outer extremity thereof. The collar 200 is resiliently urged into engagement with the valve stem shoulder by means of a coil spring 208 having one end in engagement with the collar and the opposite end thereof in engagement with a washer 210 adjustably fixed to the outer extremity of the valve stem end portion 262, as by nuts 212.

P'ivotally mounted on the bracket 1%, as by a pivot pin 214,.i-s a latch member 216 having its free end formed in a hook-shaped configuration, as indicated at 213, for engaging the surface of the annular collar flange 204 1'8 facing toward the end plate 146. The latch member is resiliently urged into a position of engagement with the outer periphery of the flange 204 by a coil spring 220 having one end suitably connected to the latch member intermediate its ends and the opposite end thereof suitably fixed to the bracket 1%.

Mounted in cooperating relation with the latch member 216 to engage the latter inter-mediate its ends and effect movement thereof in a direction opposite from the direction of bias of the spring 220 is a trip lever 222. As shown in FIGURE 7, one end of the trip lever 222 is positioned to engage the latch member 216 intermediate its ends. The opposite end of the trip lever is pivotally connected to conventional structure of the casting machine to be actuated in response to the movement of such structure in a manner hereinafter to be more fully described. Preferably, the trip lever is spring biased as by a coil spring 224 to move in a direction toward the latch member 116. In addition, trip lever 222 is capable of limited pivotal movement about a vertical axis and a coil spring 226 serves to resiliently bias the trip lever in a clockwise direction as viewed in FIGURE 7. As shown, the coil spring 226 has one end thereof suitably connected to the trip lever intermediate the ends of the latter and its opposite end suitably connected to the valve mechanism 24.

The linkage mechanism 26 includes means for delay ing the engagement of the trip lever with the latch member for one revolution of the main cam shaft of the casting machine after the actuation of the trip lever in response to a given signal to the casting machine. To this end, the trip lever has a portion adjacent the latch member engaging end thereof offset, as indicated at 228, and a stop plate 230 and guide plate 232' are mounted on opposite sides of the trip lever inwardly of the offset portion 223. The stop plate 234) is arranged to cooperate with a stop block 234 which is suitably mounted on the upper surface of the bracket 196. The surface of the stop block 234 facing the stop plate 230 is undercut in a vertical direction to provide a vertical stop shoulder 236 on the stop block for engaging the end surface of the stop plate facing toward the offset end portion 228 of the trip lever. The trip lever is maintained in the vertical plane of the latch member by means of a lower guide block 238 secured to and extending laterally from the stop block 234 and an upper iguide plate 240 fixed to the upper sur face of the stop block 234,-by any suitable means, such as bolt 24-2 or the like, and extending laterally outwardly over the upper surface of the trip lever. It will be seen that the trip lever is normally spring urged by springs 224 and 226 so as to move in a direction to engage the end of the stop plate 230 with the shoulder 236 of the stop block 234.

In order to move the trip lever from the position of engagement of the stop plate 23b with the stop block 234, the arm 19% has pivoted to the outer end thereof, as indicated at 244*, a timing finger 246. One end of the finger is pivoted to the arm at the pivot 244 and the opposite end portion thereof is disposed within a transversely extending groove 248 formed in the upper surface of the stop block 234. It will be noted that the groove 24% is of a width greater than the width of the timing finger so that it can have limited transverse movement with respect to the groove. The timing finger is resiliently biased to engage the wall of the groove remote from the latch member by means of a coil spring 250 having one end connected with the timing finger and its opposite end connected with the valve mechanism adjacent the coil spring.

Operation of the Valve Mechanism and Linkage lllechanism in Controlling the Pump Mechanism An understanding of the manner in which the linkage mechanism of the present invention is coordinated with and cooperates With the conventional structure of a Monotype casting machine can best be gained by reference to the Monotype manual mentioned above. The trip lever 222 disclosed in the present application corresponds to and takes the place of the lever a49DD, shown on pages 59 and 232 of the manual. It will be noted that in the present drawings the end of the trip lever opposite from the latch member engaging end thereof is shown connected with a link a48DD which corresponds with the same link illustrated in the manual at the above pages. It should also be noted that the trip lever 222 of the present invention extends from the link (148131) in a direction opposite to that of the link a49DD shown in the manual. Thus, the present trip lever 222, as noted above, is resiliently urged in a direction to engage the latch member 216.

While a detailed description of the movement of the link a48DD in the normal operation of the casting machine is not considered to be essential to an understanding of the operation of the present invention, it can be briefly stated that this link is moved in a direction to effect a movement of the trip lever 222 away from the latch member in response to each justification signal fed to the casting machine. Usually, justification signals will be given at the beginning of each line, although it is possible to have a plurality of justification signals within any given line. Moreover, usually two revolutions of the main cam shaft of the casting machine are required to complete the entire justification signal, that is one j justification signal and a subsequent I justification signal, although in some instances the entire justification signal can be given during one revolution of the main cam shaft of the casting machine. The operation of the casting machine is such that the mechanism utilized to effect movement of the matrix case from left to right is also utilized to effect movement of the justification wedges in response to the justification signal. Moreover, as noted above, the matrix case moving mechanism requires two complete revolutions of the main camshaft to perform the function of positioning the matrix case or the justification wedges although a signal is given each revolution. Therefore, when a justification signal is received by the machine, the pump mechanism should not be actuated in the following revolution of the cam shaft of the machine since the matrix case cannot be properly positioned in that revolution, due to the utilization of the matrix case positioning mechanism from left to right in positioning the justification wedges.

With the above in mind, and referring now more particularly to FIGURE 7, the parts of the linkage mechanism 26 are shown therein in the position they will assume between two successive justification signals. It will be noted that the trip lever 222 has been moved away from engagement with the latch member 216 and that the hooked end 218 of the latter is in engagement with the flange 264 (due to the previou justification signal) so as to maintain the valve mechanism in a position which permits air under pressure to move into the upper end of the cylinder 96 of the fluid pressure device 20, thus maintaining the pump mechanism in an inoperative position preparatory to the next operative or pumping stroke thereof. The trip lever 222 is shown in the position to which it is moved in response to the second successive justification signal. During the revolution of the main cam shaft of the machine corresponding with this justification signal, the arm 198 Will be oscillated in a direction to move the rounded portions 206 away from and then toward the collar flange 2%, however, due to the engagement of the latch member with the flange 204 the valve mechanism will not be moved during this revolution so that the pump remains inactive. It will be noted that this revolution of the main cam shaft of the machine is the revolution following the first justification signal revolution, so that the pump is inactive in the second revolution in response to the first justification signal.

Assume now that therevolution of the main cam shaft of the machine following the second successive justification signal revolution thereof is accompanied by a type character signal. This first type character signal will serve to release the trip lever 222 sothat the latter can move toward the latch member 216 under the action of coil springs 224 and 226. However, the trip lever cannot move into a position of engagement with the latch member during the first type character signal revolution due to the engagement of the end surface of the stop plate 239 with the shoulder 236 of the stop block. Also, during the first type character signal revolution the arm 198 will be oscillated in the manner indicated above and again, since the hooked end 218 of the latch member is in engagement with the flange 204 there will be no movement of the valve mechanism and hence the pump will be inactive during the revolution of the main cam shaft of the machine following the second successive justification signal revolution. It will be noted that during the oscillation of the arm 198 in the first type character signal revolution of the main cam shaft, the timing finger will be moved into the position shown in FIGURE 8 so that as the arm completes its oscillation, the end of the timing finger will engage the stop plate 230 and move the end thereof out of engagement with the stop block shoulder 236, thus permitting the trip lever to move into engagement with the latch member, as shown in FIGURE 9. The coil spring 224 which resiliently urges the trip lever into engagement with the latch member is of a force sutficient to overcome the force of the coil spring 220 which resiliently biases the latch member into a position of engagement with the flange 204. Thus, at the completion of the first type character signal rotation, the trip lever 222 will move the latch member into a position wherein the hooked end 218 is out of engagement with the flange 294, as shown in FIGURE 9.

In the following revolution of the cam shaft, that is, the revolution immediately subsequent to the first type character signal revolution which may be assumed to be a second type character signal revolution, the valve stem 150 of the valve mechanism will be moved to the left, as viewed in FIGURE 9, under the action of the coil spring 174 during the oscillation of the arm 198 to reverse the flow of air under pressure to the device so that air under pressure will enter the lower end of the cylinder 96 and move the piston rod upwardly to thus cycle the pumping mechanism in the manner previously described.

The trip lever will remain in the position shown in FIG- .URE 9 during each subsequent cam shaft revolution causing'the pump to eject type metal in response to the type character signals until the next justification signal is received. The movement of the arm 198 is timed in relation to the movement of the trip lever in response to a justification signal such that the collar flange will move before the latch member is released by the trip lever and therefore, the valve mechanism will be cycled (to complete the type metal ejection for the last type character signal) during the first justification signal revolution. However, it will be noted that the latch member is fully released during the latter part of the first justification signal revolution so that as the collar is returned the flange thereof will be engaged by the hooked end 218, as shown in FIGURE 7, to prevent movement of the valve stem during the next revolution in the manner previously described.

It can thus be seen that the linkage mechanism 26 is effective to delay the actuation of the pump mechanism one revolution of the main cam shaft of the machine after the signal for such actuation is given. When a justification signal is received during a given revolution of the cam shaft, the pump will be inactive in the following revolution of the cam shaft. When a type character signal is received during a given revolution of the cam shaft, the pump will be active in the, followingrcvolution in the cam shaft. It will also be recognized that when the line cancelling mechanism mentioned in the Monotype manual on page 67 is effective in response to a line cancelling or line killing justification signal, the trip lever 222 will be maintained in the position shown in FIGURE 7 so that the pump will be ineffective until the revolution following the first type character signal revolution in the next line (following the justification signal revolution or revolutions of such line).

In connection with the line killing function of the Monotype casting machine wherein the pump mechanism is maintained inactive for some period of time, this inactivity of the pump can have a detrimental effect on the type cast when the pump again begins operation. Indeed, any time the pump is shut down for a period of time there is the attendant possibility that the temperature of the mold will change, since molten metal is not being periodically pumped into the cavity thereof. In normal circumstances, cooling water'flows through the mold to maintain the same at as constant a temperature as possible so that the size of the cavity will remain as constant as possible for any given character. The usual effect of pump inactivity is to cast larger characters when opera tion is again commenced. Thus, these larger characters when placed together to form a line have a total dimension in excess of the galley dimension and the machine is automatically stopped under these conditions unless manually adjusted. This occurrence is so prevalent that many operators as a common practice will throw out the first line of type produced by the casting machine and then reset the tape to re-run the first line so that it will be cast at the proper size. The procedure is also necessitated frequently after a line killing operation.

The present linkage mechanism 26 lends itself quite readily to the provision of a system for controlling the flow of cooling liquid through the mold in response to the operation of the pump mechanism. While systems of this general type have been known to be embodied on standard Monotype casting machines by individual operators, the present arrangement lends itself so readily to such a system that it can be produced as standard equipment. Such a system preferably embodies an arm secured to the latch member and extending outwardly from the pivot thereof in a direction opposite from the hooked end 218. This arm is disposed in the path of movement of a microswitch which is opened when the latch member is disposed in the position shown in FIG- URE 7 and closed when the latch member is disposed in the position shown in FIGURE 9. The microswitch is connected in a circuit with a solenoid actuated valve toenergize the solenoid when closed and de-energize the solenoid when opened. The solenoid valve is connected in series with the cooling liquid flow line at a position upstream from the mold and has at least two positions of operation. One is a fully open position wherein the solenoid is energized which permits full normal flow of the cooling liquid through the mold. The other position is one in which the solenoid is de-energized and the flow of cooling liquid to the mold is restricted to a desired amount which would tend to maintain the mold at its normal operating temperature, taking into consideration the radiation heat from the molten metal in the melting pot ad jacent the mold. It will also be noted that with the system described above the solenoid actuated valve will be moved into a position to restrict flow of cooling liquid even during the one or two revolutions when the pump is inactive as a result of justification signals in the normal operation of the casting machine.

It thus will be seen that the objects of this invention have been fully and eifectively accomplished. It will be realized, however, that the foregoing specific embodiment has been shown and described only for the purpose of illustrating the principles of this invention and is subject to extensive change without departure from such principles. Therefore, this invention includes all modifications encompassed within the spirit and scope of the following claims.

I claim:

l. A pump mechanism comprising a pump body having a pump chamber and a discharge outlet communicating with said pump chamber; a pump plunger mounted for movement with respect to said pump body and said pump chamber to effect movement of liquid from said chamber outwardly through said discharge outlet; means mounting said pump body for movement between an operative position wherein said discharge outlet is disposed in substantially fluid-tight communication with a receptacle for receiving the liquid moved outwardly through said discharge opening and an inoperative position wherein said discharge outlet is disposed in spaced relation with respect to the receptacle; motion transmitting means operatively connected with said pump body and said pump plunger for effecting movement of said pump body from said inoperative position to said operative position, an initial movement of said pump plunger in a direction to move liquid outwardly of said discharge opening prior to the movement of said pump body into said operative position, and a subsequent movement of said pump plunger in a direction to move liquid outwardly of said discharge opening after the movement of said pump body into said operative position; and means for moving said motion transmitting means.

2. A pump mechanism as defined in claim 1 including a fixed abutment facing in the direction of discharge of said discharge outlet, and a plunger member carried by said pump body in communication with the liquid therein for movement in a direction away from said nozzle and into engagement with said abutment in response to the liquid discharge movement of said pump plunger to thereby apply an opposing force counteracting the force applied to said pump body by the ejection of liquid from said discharge outlet.

3. A pump mechanism as defined in claim 1 wherein said means for moving said motion transmitting means comprises a fluid pressure actuated piston and cylinder device. I

4. A pump mechanism as defined in claim 3 including a valve mechanism movable between at least two positions for reversing the flow of a fluid under pressure to said piston and cylinder device.

5. A pump mechanism as defined in claim 1 including cyclically operated means for effecting movement of said valve mechanism between said two positions during each cycle thereof and a plurality of movable members mounted in cooperating relation with respect to each other-and with respect to said cyclically operated means to be selectively set into motion during one cycle of said cyclically operated means for selectively permitting or preventing movement of said valve mechanism by said cyclically operated means during the next cycle thereof.

6. A pump mechanism comprising a pump body having a pump chamber and a discharge nozzle communicating with said pump chamber; a pump plunger mounted for movement with respect to said pump body and said pump chamber to effect movement of liquid from said chamber outwardly of said nozzle; means mounting said pump body for movement between an operative position wherein said nozzle is disposed in substantially fluid-tight communication With a receptacle for receiving the liquid moved outwardly through said nozzle and an inoperative position wherein said nozzle is disposed in spaced relation with respect to the receptacle; means for effecting movement of said pump body into said operative position and said pump plunger in a direction to move liquid outwardly of said nozzle; a fixed abutment facing in the direction of discharge of said nozzle; and a member carried by said pump body in communication with the liquid therein for movement in a direction away from said nozzle and into engagement with said abutment in response to liquid discharge movement of said pump plunger to thereby apply an opposing force counteracting the force applied to said nozzle by the ejection of liquid therefrom.

7. A pump mechanism as defined in claim 6 wherein said pump body and said pump plunger movement effecting means comprises a fluid pressure actuated piston and cylinder device, and motion transmitting means operatively connected with said device and with said pump body and said pump plunger for effecting movement of the latter in response to the movement of said device.

8. A pump mechanism as defined in claim 6 including a valve assembly movable between at least two positions for controlling the actuation of said device, cyclically operated means for effecting movement of said valve assembly between said two positions during each cycle thereof, and a plurality of :movable members mounted in cooperating relation with respect to each other and with respect to said cyclically operated means to be selectively set into motion during one cycle of said cyclically operated means for selectively permitting or preventing movement of said valve assembly by said cyclically operated means during the next cycle thereof.

9. Apparatus of the type described comprising a frame; a type metal melting pot carried by said frame; a pump body disposed in said pot and having a pump chamber,

an inlet communicating said chamber with the interior of said pot, and a discharge nozzle communicating with said chamber and extending above said pot; a pump plunger mounted for reciprocating movement with respect to said pump body and said pump chamber to effect movement of molten type metal from said pot through said inlet into said chamber during movement in one direction and to eflect movement of molten type metal from said chamber outwardly of said nozzle during movement in the other direction; means mounting said pump body on said pot for movement between an operative position wherein said nozzle is disposed in substantially fluid-tight communication with a type mold and an inoperative position wherein said nozzle is disposed in spaced relation to the type mold; a fluid pressure actuated device carried by said frame; a pair of lever arms; a link pivotally interconnected between said arms intermediate the ends thereof, means connecting the ends of one of said lever arms with said pump plunger and said device respectively; and means connecting the ends of the other of said lever arms with said pump body and said frame respectively, said device being movable in one direction to effect movement of said pump body into said operative position through movement of both lever arms and said link and movement of said pump plunger in said one direction through pivotal movement of said one lever arm about its pivot with said link initially prior to and then subsequently after the movement of said pump body into said operable position, said device being movable in the opposite direction to move said pump plunger in said other direction and said pump body into said inoperative position.

10. Apparatus as defined in claim 9 wherein said discharge nozzle extends vertically upwardly and moves upwardly into said operative position and wherein said pump body has a plunger member mounted therein for limited vertical reciprocating movement in communication with the molten type metal within said pump body, said plunger member being movable in a direction away from said nozzle and into engagement with the interior of said pot in response to the movement of said pump plunger in said one direction to thereby apply an opposing force counteracting the force applied to said nozzle by the ejection of molten type metal therefrom.

11. Apparatus as defined in claim 9 wherein said pump body mounting means comprises mounting arms extending laterally outwardly from said pump body, said mounting arms having generally horizontally aligned recesses formed in the lower surface thereof, and projections extending upwardly from said pot engaging within said 16 recesses and providing a horizontal pivotal axis for said pump body.

12. Apparatus as defined in claim 11 including counterbalancing spring means connected between said pot and said pump body mounting arms disposed in spaced relation with respect to the pivotal axis of said pump body in a direction opposite from the extent of said pump body therefrom.

13. Apparatus as defined in claim 9 wherein said one lever arm connecting means comprises a pivotal connection between said device and said one lever arm vertically reciprocable in response to the movement of said device in said directions and a cam and slot connection between said pump plunger and said one lever arm for effecting vertical reciprocating movement of said pump plunger in response to pivotal movement of said one lever arm, and wherein said other lever arm connecting means comprises a vertically fixed pivotal connection between said frame and said other lever arm and a cam and slot connection between said pump body and said other lever arm for effecting movement of said pump body between said operative and inoperative positions in response to pivotal movement of said one lever arm.

14. Apparatus as defined in claim 13 including means mounting said pot on said frame for swinging movement about a vertical axis and vertical movement along said axis, the pivotal connections of said arms being mounted for swinging movement about a common vertical axis spaced from the vertical swinging axis of said pot in a direction with respect to the latter opposite from the extent of said pot.

15. Apparatus as defined in claim 9 wherein said fluid pressure actuated device comprises a piston and cylinder unit and wherein a valve assembly is operatively connected with said piston and cylinder unit for movement into two positions to reverse the flow of a fluid under pressure to said piston and cylinder unit.

16. Apparatus as described in claim 15 including cyclically operated means for effecting a movement of said valve assembly between said two positions during each cycle thereof, and a plurality of movable members mounted in cooperating relation with respect to each other and with respect to said cyclically operated means to be selectively set into motion during one cycle of said cyclically operated means for selectively permitting or preventing movement of said valve assembly by said cyclically operated means during the next cycle thereof.

17. Apparatus as defined in claim 16 wherein said valve assembly includes a valve stem spring biased for movement into one of said positions and movable against such spring bias into the other of said positions, one of said movable members comprising a flanged collar carried by said valve stem, another of said movable members comprising a latch member pivotally biased for movement into a position to engage said flanged collar, still another of said movable members comprising a trip lever mounted for spring biased movement in a direction to engage said latch member and move the latter out of engagement with said flanged collar, abutment means disposed in the biased path of movement of said trip lever for preventing movement of said trip lever into engagement with said latch member, said cyclically operated means including an arm mounted for oscillatory movement in the path of movement of said flanged collar for engaging the latter and ettecting opposed spring biased movement of said valve stem during the oscillatory movement of said arm in one direction and to permit spring biased movement of said valve stem during the movement of said arm in the opposite direction when said latch member is disposed in a position out of engagement with said flanged collar, said arm having a timing finger connected therewith and guided for movement during the oscillatory movement of said arm into the path of movement of said trip lever when the latter is disposed in engagement with said abutment means to thereby permit the trip lever to move into spring pressed engagement with said latch member.

18. Apparatus of the type described comprising a frame; a type metal melting pot carried by said frame; a pump body disposed in said pot and having a pump chamber, an inlet communicating said chamber with the interior of said pot, and a discharge nozzle communicating with said chamber and extending above said pot; a pump plunger mounted for reciprocating movement with respect to said pump body and said pump chamber to effect movement of molten type metal from said pot through said inlet into said chamber during movement in one direction and to effect movement of molten type metal from said chamber outwardly of said nozzle during movement in the other direction, means mounting said pump body on said pot for pivotal movement about a horizontal axis spaced horizontally from said nozzle between an operative position wherein said nozzle is disposed in substantially fluid-tight communication with a type mold and an inoperative position wherein said nozzle is disposed in spaced relation to the type mold; a fluid pressure actuated device carried by said frame; motion transmitting means operatively connected with said device and with said pump body and pump plunger for effecting movement of said pump body into operative position and movement of said pump plunger in said one direction during the movement of said device in one direction and for effecting movement of said pump body into said inoperative position and said pump plunger in said other direction during the movement of said device in the opposite direction; said pump body having a plunger member mounted therein in communication with the molten type metal in said pump body for limited vertical reciprocating movement, said plunger member being movable into engagement with the interior of said pot in response to the movement of said pump plunger in said one direction to thereby apply an opposing force counteracting the force applied to said nozzle by the ejection of type metal therefrom.

19. A valve actuating mechanism comprising a valve assembly movable between at least two positions, cyclically operated means for effecting movement of said valve assembly between said two positions during each cycle thereof, and a plurality of movable members mounted in cooperating relation with respect to each other and with respect to said cyclically operated means to be selectively set into motion during one cycle of said cyclically operated means for selectively permitting or preventing movement of said valve assembly by said cyclically operated means during the next cycle thereof.

20. A valve actuating mechanism as defined in claim 19 wherein said valve assembly includes a valve stem spring biased for movement into one of said positions and movable against such spring bias into the other of said positions, one of said movable members comprising a flanged collar carried by said valve stem, another of said movable members comprising a latch member pivotally biased for movement into a position to engage said flanged collar, still another of said movable members comprising a trip lever mounted for spring biased movement in a direction to engage said latch member and move the latter out of engagement with said flanged collar, abutment means disposed in the biased path of movement of said trip lever for preventing movement of said trip lever into engagement with said latch member, said cyclically operated means including an arm mounted for oscillatory movement in the path of movement of said flanged collar for engaging the latter and effecting opposed spring biased movement of said valve stem during the oscillatory movement of said arm in one direction and to permit spring biased movement of said valve stem during the movement of said arm in the opposite direction when said latch member is disposed in a position out of engagement with said flanged collar, said arm having a timing finger connected therewith and guided for movement during the oscillatory movement of said arm into the path of movement of said trip lever when the latter is disposed in engagement with said abutment means to thereby permit the trip lever to move into spring pressed engagement with said latch member.

References Cited in the file of this patent UNITED STATES PATENTS 2,243,835 Brunner et a1. June 3, 1941 

1. A PUMP MECHANISM COMPRISING A PUMP BODY HAVING A PUMP CHAMBER AND A DISCHARGE OUTLET COMMUNICATING WITH SAID PUMP CHAMBER; A PUMP PLUNGER MOUNTED FOR MOVEMENT WITH RESPECT TO SAID PUMP BODY AND SAID PUMP CHAMBER TO EFFECT MOVEMENT OF LIQUID FROM SAID CHAMBER OUTWARDLY THROUGH SAID DISCHARGE OUTLET; MEANS MOUNTING SAID PUMP BODY FOR MOVEMENT BETWEEN AN OPERATIVE POSITION WHEREIN SAID DISCHARGE OUTLET IS DISPOSED IN SUBSTANTIALLY FLUID-TIGHT COMMUNICATION WITH A RECEPTACLE FOR RECEIVING THE LIQUID MOVED OUTWARDLY THROUGH SAID DISCHARGE OPENING AND AN INOPERATIVE POSITION WHEREIN SAID DISCHARGE OUTLET IS DISPOSED IN SPACED RELATION WITH RESPECT TO THE RECEPTACLE; MOTION TRANSMITTING MEANS OPERATIVELY CONNECTED WITH SAID PUMP BODY AND SAID PUMP PLUNGER FOR EFFECTING MOVEMENT OF SAID PUMP BODY FROM SAID INOPERATIVE POSITION TO SAID OPERATIVE POSITION, AN INITIAL MOVEMENT OF SAID PUMP PLUNGER IN A DIRECTION TO MOVE LIQUID OUTWARDLY OF SAID DISCHARGE OPENING PRIOR TO THE MOVEMENT OF SAID PUMP BODY INTO SAID OPERATIVE POSITION, AND A SUBSEQUENT MOVEMENT OF SAID PUMP PLUNGER IN A DIRECTION TO MOVE LIQUID OUTWARDLY OF SAID DISCHARGE OPENING AFTER THE MOVEMENT OF SAID PUMP BODY INTO SAID OPERATIVE POSITION; AND MEANS FOR MOVING SAID MOTION TRANSMITTING MEANS. 